Transmission and control system



June 23, 1970 F, DICKENBROCK 26,917

TRANSMISSION AND CONTROL SYSTEM Original Filed March 21, 1966 5Sheets-Sheet IT N'V ENTOR. "er/2A fizckezzrock A M Z 57 W7///// Q MM//%l A f///////// N/ r/ \w\\ \r N June 23, 1970 F. DICKENBROCK Re. 26,917

TRANSMISSION AND CONTROL SYSTEM 5 Sheets-Sheet},

Original Filed March 21, 1966 ATTORNEY F. DICKENBROCK Re. 26,917

TRANSMISSION AND CONTROL SYSTEM June 23, 1970 3 Sheets-Sheet 15 OriginalFiled March 21 ROLLER SPW m D E TE I UP OS V ROL l i R ROLLER SPIN AXISV RACE ROLLER SPIN RACE AXIS A: TORNZ United States Patent Oflice Re.26,917 Reissued June 23, 1970 26,917 TRANSMISSION AND CONTROL SYSTEMFrank Dickenhrock, Warren, Mich., assignor to General MotorsCorporation, Detroit, Mich., a corporation of Delaware Original No.3,394,617, dated July 30, 1968, Ser. No. 535,824, Mar. 21, 1966.Application for reissue May 6, 1969, Ser. No. 830,893

Int. Cl. F16h 47/08, /50, 15/38 US. Cl. 74730 16 Claims Matter enclosedin heavy brackets appears in the original patent but forms no part ofthis reissue specification; matter printed in italics indicates theadditions made by reissue.

ABSTRACT OF THE DISCLOSURE A roller friction transmission having twofriction units and a hydrodynamic torque converter wherein a commoninput race for both friction units is driven by the converter turbine,wherein the reaction torque of the torque converter and the reactiontorque of one friction roller unit are both transmitted to thetransmission case through the reaction spider of the other frictionunit.

This invention relates to transmissions and more particularly to afriction roller transmission adapted to provide infinitely variablechanges of drive ratio, and the control system for controlling the drivetransmission drive ratio.

The control system herein disclosed provides a simple roller mount whichwill allow the roller to be steered to its correct tilt position by lowamplitude forces with large tractive forces serving as the primaryforces acting to tilt the roller. A small force, only, is necessary toincline the roller and this inclination produces a large tractive forcetrying to tilt the roller. In addition, the control system automaticallyreduces the roller inclination to zero when the desired tilt angle isreached. The roller mount, in addition, provides a path for lubrication,limits the rate of ratio change, and prevents undesirable ratio change.The control system is arranged such that the rate of tilt change isproportional to the difference between the desired and actual rollertilt. The control system will correct any tendency of the rollers toovershoot or to wander in tilt. In addition, the control system isunaffected by axial deflections and can be adjusted for both axial andcircumferential tolerance errors.

These and other features and advantages of the invention will beapparent from the following specification and claims taken inconjunction with the accompanying drawings in which:

FIGURE 1 is a longitudinal partially sectional view through atransmission incorporating the features of this invention;

FIGURE 1a is a top plan view of a helical groove provided on a driveratio control sleeve;

FIGURE 2 is a sectional view through the roller mount and controlassembly;

FIGURE 3 is a schematic diagram illustrating the rollers positioned toprovide a direct drive or 1:1 drive ratio;

FIGURE 3a is a schematic diagram illustrating the rollers in overdriveor speed multiplying position;

FIGURE 3b is a schematic diagram illustrating the rollers in underdriveor torque multiplying position;

FIGURE 4 is a diagrammatic illustration of an input end viewillustrating the roller and race velocities when the roller inclinationis zero;

FIGURE 4a is a diagrammatic illustration of a longitudinal viewillustrating the roller and race velocities when the roller inclinationis zero;

FIGURE 4b is a diagrammatic illustration of an output end viewillustrating the roller and race velocities when the roller inclinationis zero;

FIGURE 5 is a diagrammatic illustration of an input end viewillustrating the roller and race velocities with the roller inclinedsuch that the roller spin axis is inclined with respect to the raceaxis; and

FIGURE 5a is a diagrammatic illustration of an output end vieyillustrating the roller and race velocities with the roller inclinedsuch that the roller spin axis is inclined with respect to the raceaxis.

Referring initially to FIGURE 3, there is shown schematically theroller-race feature of a friction transmission having a power inputshaft 11 connected to drive a central power input race 23 through a drum22. Front and rear rollers 51 and contact opposite sides of race 23 andcontact driven races 52 and 53 which deliver power to a power deliveryshaft 60. In the race position shown, output shaft will be driven at thesame speed as input shaft 11 or at a 1:1 drive ratio.

With the rollers positioned as shown in FIGURE 3a output shaft 60 willbe driven faster than inputrace 23 or in overdrive or speed multiplyingratio. The rollers may also be positioned in FIGURE 3b to provideunderdrive of shaft 60 or to provide torque multiplying ratio. It willbe understood that within the range of operation of the device therollers may be placed in various positions with respect to the drivenraces to provide an infinite number of ratios of overdrive or underdriveas well as direct drive of output shaft 60.

FIGURES 3, 3a, 3b illustrate the rollers in various operative positionswith dr'flerent till angles to provide difi'erent ratio drives but notthe method or structure for tilting them to such positions. It ispossible to change roller position simply by shoving or forcing theminto a desired position. Such a method is undesirable because itrequires high forces and has slow response. As distinguished from thismethod, the rollers may be steered to a tilt angle by use of arelatively minor force.

In FIGURES 4, 4a, 4b, the relative [velocity] velocities of the racesand rollers [is] are illustrated for an operating condition wherein theroller are placed in a first of two possible positions. This position isone wherein the spin axis of the roller intersects the race axis at thecenter of the roller 01' midway between the races and the roller simplyspins with no other movement. The roller and race velocities are equalas illustrated by the vectors. for the condition of zero inclination ofthe rollers with respect to the races.

In FIGURES 5 and 5a the effect of inclining the rollers With respect tothe races is illustrated by appropriate vectors V-race, V-roller. Asillustrated, the roller spin axis is inclined with respect to the raceaxis by the angle a. The vectors illustrate [illustrated] the race androller velocities for an inclination of a given angle. It can be seenthat inclining the roller moves its spin axis away from the race axis.The roller will tend to match the race velocity and will do this bytilting to generate the necessary velocity components. Only a smallforce is necessary to incline the roller and this inclination produceslarge tractive forces trying to tilt the roller. The control systemhereafter described makes use of the above principle and in additionautomatically reduces the roller inclination to zero when the desiredtilt angle is reached.

Referring to FIGURE 1 there is shown a transmission 10 incorporating aroller control system utilizing initial roller inclination [tilt] [arelatively small force) and roller tractive effort (a relatively largeforce) to change the tilt angle of the rollers to any desired tiltangle.

An engine driven power input shaft 11 drives a drum 12 rotatablysupported in a transmission housing 13 by a bearing 14. An axial sleeve16 supported in bearing 14 drives a pump 17 adapted to provide oil underpressure for transmission control and lubrication purposes. A seal 18 isdisposed between web and sleeve 16 and oil return passages 19 areprovided in the web. A housing section 20 is bolted to housing 13 bybolts 21. A race drive drum 22 splined to a power input race 23 drivesrace 23 whenever engine driven power input shaft 11 is rotated.

A rear spider 25 shown in FIGURES 1 and 2 is splined to case section 20and is held against rotation by splines 26 on the spider. Spider 25comprises a ring in which are supported three masts 27, each mastsupporting a roller 50 as best shown in FIGURE 2. Each mast is formedwith a ball head 28 for receiving a roller carrier 29. Each roller 50 isrotatably supported on carrier 29 by means of a bushing 30. Each carrier29 is swaged to ball 28 such that ball 28 serves as a pivot point forthe carrier. Carriers 29 are provided with [a] ball-ended [extension]extensions- 31, the balls 31 each being disposed in a helical groove 32formed in a roller phasing collar 33 rotatable with central controlsleeve 34. Two pins 35 and 36 are driven into the carrier 29. These pinsprevent the carrier from spinning and wearing out its ball end, limitthe inclination of the carrier [and] to limit the rate of change ofratio to prevent too rapid ratio change, and channel lubricating oilinto the roller bushing. As shown, oil for lubrication purposes may besupplied to an annular passage 37a in spider 25 and through passage 37in masts 27 and through passages in pins 35, 36 to bushing 30.

Collar 33 may be formed integrally with control sleeve 34 or may beformed as a separate piece splined to sleeve 34. In either event themember 33 is formed with a stub shaft 40 adapted to receive a controlrod 41. Rod 41 may be moved by any suitable means such as a hydraulic[juck] jack to rotate control sleeve 34. Helical groove 32 in collar 33is preferably at a 30 helix angle, as shown in FIGURE 1a. Rod 41 may bemoved by means of any suitable linkage such as a movable bellcrank lever42 actuated by a pin 43.

Power input race 23 is rotatably supported upon a support member 44grounded to spider 25 by a web 45.

A forward unit roller 51 is supported in a spider 51a and carrierassembly similar to that already described and, accordingly, additionaldetailed description is not believed necessary. The spider 51a of theforward unit is grounded to race support member 44 by a web extension 46splined to member 44. Ground member 46 is preferably designed to haveinherent flexibility and may comprise a flexible plate. A spacer 47 isdisposed between sleeve 34 and one side of member 33 and spacers 48 and49 are disposed between race 23 and member 44.

Roller 50 contacts power input race 23 and a power delivery race 52supported upon a power delivery shaft 60. Any suitable axial loadingdevice may be used to place an axial thrust on the rollers and races tomaintain the rollers in nonslipping friction contact with the drive anddriven races. For example, a ball 54 may act in cam surfaces in race 52and in a flange 55 splined to shaft 60. Flange 55 may be held on shaftby a nut 56. Oil for axial loading purposes may be supplied to thechamber 61 between race 52 and flange 55 by means of a passage 58 inhousing support web 57, and a passage 59 in shaft 60.

Roller 51 contacts drive race 23 and delivers power to a driven race 53,connected to shaft 60 by a spline 62, [and] the shaft 60 and race 53being provided with overlapping lips 63 and 64 which absorb the axialthrust placed on race 53 by the axial thrust loading mechanism.

Drive shaft 11 drives an impeller 65 of a hydrodynamic torque converterhaving a turbine 66 and a bladed reactor 67, the converter assemblybeing indicated generally at 70. Reactor 67 is grounded against reverserotation by means of a one-way brake 68 and a ground sleeve 69 splinedto spider 51a of the front roller unit. Turbine 66 is splined to a drivesleeve 71 which, in turn, is splined to race drive drum 22. Output shaft60 is piloted in the hub 72 of impeller 65 while hub 72 is piloted incrankshaft 11. Bushings 73 and 74 are disposed between hub 72 and shaft60 and between hub 72 and crankshaft 11. Shaft 60 may drive a forwardand reverse gear unit (not shown) which in turn may drive the vehiclewheels, not shown.

The features heretofore described, including the arrangement of thecontrol sleeve and helical slot, and ball ends for causing the rollersand carriers to incline is believed novel. The direction of the helicalslots is so arranged that as the rollers tilt the slot and ball pincoact to tend to reduce this inclination of the rollers. Tilt of therollers will continue until this inclination is zero. If any overshootor wander from a desired tilt position occurs, the carrier ball end willmove in the slot or helical groove and produce an inclination tending toautomatically return the roller to its desired position. Since theinclining of the roller moves its spin axis away from the race axis asexplained in connection with FIGURES 5. 5a, the roller will tend tomatch the race velocity and will do this to generate the necessaryvelocity compo nents. The control system therefore also produces a rateof tilt correction or change which is variable and is proportional tothe difference between the desired and actual tilt position. The rate oftilt correction will be relatively large when the difference between thedesired tilt position and the actual tilt position is relatively greatand will automatically decrease as the roller approaches the desiredtilt position, due to the varying tractive forces generated at therollers edges resulting from the progressively varying inclination ofthe rollers.

The spacer 47 in FIGURE 1 provides a convenient means for making initialadjustments for manufacturing tolerance errors such that the ratios ofthe two roller units will be the same. Due to manufacturing toleranceerrors in making the carriers and control sleeve mechanism these axialand circumferential tolerances may result in an assembly wherein theratios of the two roller units are not the same. The spacer 47 may beselected to correct for both of these errors since it shifts theposition of the helical grooves. More specifically, the spacer may beselected of proper width to shift the position of the grooves relativeto each other to assure that the ratios of the roller units are thesame.

As heretofore stated, the front unit spider [25] 51a which is notrigidly fixed to the case is supported torsionally and axially by asupport member 46 which comprises a flex plate. The normal contact loadtends to deflect the two roller sections axially. Accordingly, some partmust be able to accommodate this deflection to revent the rollerbushings from being excessively loaded. The floating front unit spider[25] 51a allows movement. Although this movement will tend to shift thefront unit carrier ball 31 in its helical groove 32, this can be avoidedby designing the necessary torsional flexibility into the front spider[25] 51 and designing the front unit flex plate to have proper stiffnessto prevent ratio change due to axial loading.

There has been provided a novel control system incorporating a simpleroller mount which will allow the roller to be steered into its correcttilt position by low amplitude forces. This roller mount provides a pathfor lubrication, limits the rate of ratio change and preventsundesirable carrier spinning. The control system is so constructed thatthe rate of roller tilt change is variable and proportional to thedifference between the desired and actual roller tilt. The controlsystem will automatically correct any tendency of the rollers to wanderor overshoot in tilt. The control system is unaffected by axialdeflections and can be adjusted for both axial and circumferentialtolerance errors to assure that the ratios of both friction units arethe same. The torque converter impeller 65 is driven at engine speed andthe reaction torque from reaction member 67 is grounded to the casethrough spider [25a] 51a, flexible plate 46, support member 44, plate45, and rear spider 25 to housing section 20.

The arrangement whereby the torque converter reaction torque istransmitted to the front unit floating spider and the reaction from thefront unit spider are transmitted to the rear unit spider through sleeve44 and flexible plate connectors 46 and 45 is also believed novel.

I claim:

1. In a transmission, a case, an output shaft, an engine driven powerinput race for driving first and second roller units, each of saidroller units including a power delivery race fixed for rotation as aunit with said output shaft and a disc roller for transmitting torquebetween said input race and said output [shafts] shaft, respectively,each of said units including a reaction spider comprising an annularring, means grounding the exterior periphery of the spider ring of thefirst of said units directly to said case, a support member concentricwith said output shaft for rotatably supporting said input race, meansconnecting the reaction spider ring of said second unit to said inputrace support member, means connecting said input race support member tosaid first unit spider ring whereby reaction torque of said second unitspider is transmitted to said case through said input race supportmember and said first unit reaction spider ring, a first mast having ahub carried by said first unit spider ring and a free end extendinginwardly from said ring into the space encompassed by said ring, a ballon said free end, a roller carrier forming with said ball a swivel jointand rotatably supporting the disc roller of the first unit in contactwith said input race and said first unit power delivery race, a driveratio control sleeve, a collar on said sleeve, a helical groove in saidcollar, an extension on said carrier having a free end disposed in saidgroove, a second mast having a hub carried by said second unit reactionspider ring and a free end extending radially inwardly from said ringinto the space encompassed by said ring, a ball on said free end, asecond roller carrier supporting a disc roller for the second unit incontact with said power input race and said second unit power deliveryrace, said second carrier forming a swivel joint with said second mastball end, a second collar on said sleeve, a helical groove in saidsecond collar, an extension on said second roller carrier having a freeend disposed in said groove, and means for rotating said sleeve to tiltthe rollers of each of said units relative to said races.

2. In a transmission, a case, a hydrodynamic torque converter includingan engine driven impeller, a turbine and a reaction member, a [fritcion]friction roller unit including a power input race, a power delivery raceand a disc type roller in friction contact with said races, a supportmember for rotatably supporting said input race, a final power deliveryshaft driven by said power delivery race, a reaction spider comprisingan annular ring grounded to said case at the outer periphery of saidring, a mast having one end supported in said ring and a free endextending inwardly into the space encompassed by said ring, a ball onsaid free end of said mast, a carrier rotatably supporting said discroller, said carrier forming with said mast ball a swivel joint betweensaid mast and said carrier, a ratio control collar, a helical groove insaid collar, an extension on said carrier disposed in said groove, saidfinal power delivery shaft extending through said ratio control collarand said input race support member, means for rotating said drive ratiocontrol collar relative to said input race support member to vary thedrive ratio, means connecting said power input race to said torqueconverter turbine including a cylinder member extending from saidturbine to said power input race, means for braking said torqueconverter reaction member from rotation in at least one directionincluding a second cylinder member disposed inside said first cylindermember and fixed to said input race support member, and means connectingsaid input race support member to said reaction spider for transmittingre action torque of said torque converter reaction member to said casethrough said spider.

3. In a transmission, a case, a hydrodynamic torque converter includingan engine driven impeller, a turbine and a reaction member, [a] firstand second friction roller units, a first reaction spider for said firstroller unit comprising an annular ring secured to said case at the outerperiphery of said ring, a mast having a base supported in said ring andextending radially inwardly into the space encompassed by said ring, aball end on said ring, a roller carrier forming with said ball end aswivel joint, a disc roller rotatably supported upon said carrier, apower input race support member, a power input race rotatably supportedupon said support member, a drive ratio control sleeve rotatablysupported in said input race support member and extending through saidinput race support member, a power delivery shaft extending through saiddrive ratio control sleeve, 21 power delivery race rotatable as a unitwith said power delivery shaft, said disc roller contacting said inputrace and power delivery race for transmitting torque therebelween, anextension on said roller carrier, a drive ratio control collar fixed forrotation with said sleeve, a helical groove in said collar receivingsaid carrier extension, a second spider for said second roller unitcomprising an annular ring, a mast carried by said second spider ringhaving a free end extending radially inwardly from said ring into thespace encompassed by said ring, a ball end on said mast, a rollercarrier forming with said mast a swivel joint, a disc roller rotatablysupported on said mast, a second unit power delivery disc rotatable as aunit with said power delivery shaft, said second unit disc rollercontacting said input race and second unit power delivery race fortransmitting torque therebetwcen, a second control collar fixed to saidsleeve, a helical groove in said second collar, an extension on saidsecond unit roller carrier having a free end disposed in said groove, acylinder member connecting said turbine to said input race for drivingsaid input race, means for Preventing rotation of said torque converterreaction member in at least one direction including a second cylinderconnecting said torque converter reaction member to said second rollerunit spider, means connecting said second roller unit spider to saidinput race support member, means connecting said input race supportmember to said first unit spider whereby the reaction torque of saidtorque converter reaction member and said second roller unit istransmitted to said case through said first unit spider, and means forrotating said control sleeve relative to said input race support memberto simultaneously [titlt] tilt both of said carriers on their respectivemasts to vary the transmission drive ratio.

4. In a toric transmission including a housing; an input means; anoutput means; a toroidal power transmission mechanism comprising afriction roller assembly including first and second annular race membersand a rollcr having a circular perimeter and a central axial openingformed therein, said roller being rotatably disposed between and withopposed portions of the perimeter in frictional contact with said firstand second race members for rotation about a spin axis perpendicular to1h, plane of said circular perimeter at its center inclinaiing about aninclination axis in said plane through said opposed portions from anormal position in which the spin axis intersects the race axis andtilting about a tilting axis at right angles to said inclination axisand in said planc, a support member, one of said members beingoperative/y connected to the input means, another of said members beingopcrativcly connected to the output mcans, and the third of said membersbeing secured to said housing, said support member having a mastsupported by said support member having pivot means at the free endextending into and terminating at the center of said central axialopening, a carrier pirotably mounted on said pivot means at theintersection of said spin axis and said plane, located in said centralaxial opening and rotatably supporting said roller for rotation onlyabout said spin axis, a ratio control collar concentrically locatedrelative to said support member, a cam groove formed in said ratiocontrol collar, a rigid extension formed on said carrier and extendingaway from said mast into said cant groove, and means for moving saidratio control collar for inclining said extension, carrier and rollerabout said pivot means and along a transverse plane intermediate theplanes of said first and second races, resulting in automatic tilting ofsaid roller, carrier and extension along a plane perpendicular to saidintermediate plane for variation of the drive ratio between said inputand output means and in automatic reduction of said inclination to Zero.

5. In a toric transmission; a housing; input means and output meansrotatably mounted in said housing; a pair of annular toric race memberscoaxially mounted on a race axis with facing toric sides; a rollerhaving a circu lar perimeter located between said race members withopposed portions of the circular perimeter in frictional contact withsaid facing toric sides of said race members being rotatable about aspin axis perpendicular to the plane of said circular perimeter at thecenter thereof and biasing said spin axis to a position intersectingsaid race axis, being inclinable about an axis of inclination throughsaid opposed portions to move said spin axis away from said race axis,being tiltable to tilt said axis of inclination relative to said raceaxis, and having a central axial opening in said roller, carrier meansin said opening having first universal pivot means opening to one sideof said roller; a rigid extension rigidly fixed to said carrier meansprojecting from one side of said carrier means and roller; bearing meansbetween said carrier means and said roller to rotatably mount saidroller on said carrier means for rotation only about said spin axis; asupport member having second universal pivot means cooperating with saidfirst universal pivot means for universally pivoting movement of saidcarrier means about the point at the intersection of said spin axis andsaid plane of the circular perimeter; movable cam means cooperating withsaid extension operative on a predetermined movement for a predeterminedratio change to move said spin axis away from said race axis to inclinesaid roller to produce tractive forces to tilt the roller to change theratio drive and automatically operative in response to said inclinationto return said spin axis to said race axis to reduce the rollerinclination to Zero when said predetermined ratio change is made; onemember being operatively connected to said input means; a second beingoperatively connected to said output means and a third being operativelyconnected to said housing.

6. The invention defined in claim 5 and said cam means having a camangle to provide a rate of tilt change which is proportional to thedifference between the actual tilt position and the desired tiltposition.

7. The invention defined in claim 5 and said first and second universalpivot means having limit means for lituiting the inclination of saidcarrier means and roller member.

8. The invention defined in claim 5 and said first and second universalpivot means having antispin means preventing rotation of said carriermeans relative to said support member only about said spin axis so allrotary movement of said roller about said spin axis is provided by saidbearing means.

9. The invention defined in claim 5 and said central axial openingextending cotnpletely through said roller; said carrier means being aunitary element located in said opening; said first universal pivotmeans being a socket open to one side of said element; said rigidextension projectiug from the opposite side of said carrier means.

10. In a toric transmission including a housing, a toroidal powerttansntisiou mechanism comprising a friction roller assembly includingfirst and second annular race ntembers and a roller having a centralaxial opening formed therein, said roller being rotatably disposedbetween and with opposed portions 'of the perimeter in frictionalcontact with said first and second race members, a support member, oneof said members being operatively connected to an input means, anotherof said members being operatively connected to an output means, and thethird of said members being secured to said housing, an outer annularring, spoke tneans for securing said outer annular ring to said centralsupport member, a mast having one end thereof supported by said centralsupport member and a free end extending into and terminating at thecenter of said central axial opening, a carrier pivotably mounted onsaid free end and in said central axial opening such that said rollermay rotate thereon, a ratio control collar concentrically locatedrelative to said annular ring, a cam groove formed in said ratio controlcoller, an extension formed on said carrier and extending away from saidmast into said cam groove, and means for moving said ratio controlcollar for inclining said extension, carrier and roller about said freeend and along a plane intermediate the planes of said first and secondrace members, resulting in automatic tilting of said roller, carrier andextension along a plane perpendicular to said intermediate plane forvariation of the drive ratio between said input and output means and inautomatic reduction of said inclination to zero.

11. In a toric transmission including a housing, a toroidal powertransmission mechanism comprising a friction roller assembly includingfirst and second races and a roller having a central axial openingformed therein, said roller being rotatably disposed between said firstand second races, a central spider member, one of said first and secondraces and said central spider member being operatively connected to aninput means, another of said first and second races and said centralspider member being operatively connected to an output means, and thethird of said first and second races and said central spider memberbeing secured to said housing, an outer annular ring, spoke means forsecuring said outer annular ring to said central spider member, a masthaving one end therdof supported by said central spider member and afree ball-shaped end extending into and terminating at the center ofsaid central axial opening, a carrier pivotably mounted on saidball-shaped end and in said central axial opening such that said rollermay rotate thereon, a ratio control coller concentrically locatedrelative to said annular ring, a cam groove formed in said ratio controlcollar, an extension formed on said carrier and extending away from saidmast into said cam groove, and means for moving said ratio controlcollar for inclining said extension carrier and roller about saidballshaped end and along a plane intermediate the planes of said firstand second races and parallel thereto when said rollers are in a 1:!output/input speed ratio, resulting in automatic tilting of said roller,carrier and extension along a plane perpendicular to said intermediateplane for variation of the drive ratio between said input and outputmeans and in automatic reduction of said inclination to zero.

12. In a toric transmission including a housing, a toroidal powertransmission mechanism comprising a friction roller assembly including apower input race, a driven race, and a roller having a central axialopening formed therein, said roller being rotatably disposed between andfrictionally engaging said input and driven races, a reaction memberincluding an annular ring grounded to said housing at the outerperiphery thereof, a must having one end thereof supported by saidreaction member and a free pivotable and extending into and terminatingat the center of said central axial opening, a carrier pivotably mountedon said pivotable end and in said central axial opening such that saidroller may rotate thereon, a ratio control collar concentrically locatedrelative to said annular ring, a cam groove formed in said ratio controlcollar, an extension formed on said carrier and extending away from saidmast into said cam groove, and means for moving said ratio controlcollar for inclining said extension, carrier and roller about saidpivotable end and along a plane parallel to and intermediate the planesof rotation of said input and driven races when said rollers are in a1:1 output/input speed ratio, resulting in automatic tilting of theroller, carrier and extension along a plane perpendicular to saidintermediate plane for variation of the drive ratio between said inputand driven races and in automatic reduction of said inclination to zero.

13. In a toric transmission including a housing, a toroidalvariable-ratio power transmission mechanism comprising a friction rollerassembly including a toroidal power input race, a toroidal driven race,said input and driven races being disposed coaxially with respect to oneanother, and a roller rotatably disposed between said input and drivenraces and frictionally engaging both of said races, a reaction spiderincluding an annular ring grounded to said housing at the outerperiphery thereof, a mast having one end supported by said reactionspider and a free end extending into and terminating at the center ofsaid roller, a carrier rotatably mounted on said ,free end andsupporting said roller, a ratio control collar concentrically locatedwithin said annular ring, a cam groove formed in said ratio controlcollar, an extension formed on said carrier and disposed in said camgroove such that a predetermined rotary movement of said col lar causesinclination of said carrier, roller and extension about an axis parallelto the common axis of said races, resulting in tilting of said carrier,roller and extension toward one of said races due to the tractive forcesgenerated on the contacting edges of said roller and in automaticallyreducing the inclination to zero when the desired tilt angle is reached.

14. In a transmission having a case and a hydrodynamic torque converterincluding an engine driven impeller, a turbine and a reaction member, afriction roller unit operatively connected to said torque converter andincluding a power input race, a power delivery race and a disc typeroller in friction contact with said races, a support member forrotatably supporting said input race, a final power delivery shaftoperatively connected to said power delivery race, a reaction spidercomprising an an annular ring grounded to said case at the outerperiphery of said ring, a support mast having one end supported by saidreaction spider and a free end extending into the center of said roller,a carrier rotatably supporting said disc roller, said carrier formingwith said mast free end a swivel joint between said mast and saidcarrier, a ratio control collar, a cam groove in said collar, onextension on said carrier disposed in said cam groove, and means forrotating said drive ratio control collar relative to said input racesupport member to incline said carrier extension, said carrier and saidroller between said races, thereby producing tractive forces on thecontacting edges of said roller resulting in automatic tilting of saidroller in a radial direction along said races to vary the speed ratio.

15. In a toric transmission including a housing, a toroidal powertransmission mechanism comprising a power input race; a driven race; anda plurality of rollers, each having a central axial opening formedtherein, said rollers being rotatably disposed between and frictionallyengaging said input and driven races; a reaction member including anannular ring grounded to said housing at the outer periphery thereof; aplurality of masts, each having one end thereof supported by saidreaction member and a free ball-shaped en-d extending into andterminating at the center of one of said plurality of central axialopenings; a carrier pivotably mounted on each of said ball-shaped endsin each of said central axial openings such that one of said pluralityof rollers is rotatable thereon; a ratio control collar concentricallylocated relative to said annular ring; a plurality of cam grooves formedin said ratio control collar; an extension formed on each of saidcarriers and extending away from said masts into said cam grooves, andmeans for moving said ratio control collar for inclining saidextensions, carriers and rollers about said ball-shaped ends and along aplane intermediate the planes of rotation of said input and drivenraces, resulting in automatic tilting of the rollers, carriers andextensions along a plane perpendicular to said intermediate plane forvariation of the drive ratio between said input and driven races and inautomatic reduction of said inclination to zero, the tilting continuinguntil all the inclination is removed.

16. In a toric transmission including a housing; a toroidal continuouslyvariable-ratio power transmission mechanism comprising a toroidal powerinput race; a toroidal driven race, said input and driven races beingdisposed coaxially with respect to one another; three rollers, eachrotatably disposed between said input and driven races and frictionallyengaging both of said races; a reaction spider including an annular ringgrounded to said housing at the outer periphery thereof; three masts,each having one end supported by said reaction spider and a free endextending into and terminating at the center of one of said rollers, acarrier rotatably mounted on each of said free ends of said masts andsupporting one of said rollers; a ratio control collar concentricallylocated within said annular ring; a cam groove formed in said ratiocontrol collar in radial alignment with each of said masts; an extensionformed on each of said carriers and disposed in one of said cam groovessuch that a predetermined movement of said collar causes inclination ofeach of said carriers, rollers and extensions about an axis parallel tothe common axis of said races when said rollers are in a 1:] speed ratioposition, resulting in tilting of each of said carriers, rollers andextensions toward one of said races and in automatically reducing theinclination to zero.

References Cited The following references, cited by the Examiner, are ofrecord in the patented file of this patent or the original patent.

UNITED STATES PATENTS 1,947,044 2/1934 Goue 74-796 1,985,110 12/1934Sharpe 74200 2,108,082 2/1938 Sharpe 74796 2,113,638 4/1938 Almen 74-2OO2,131,158 9/1938 Almen et a1. 74-1905 2,182,458 12/1939 Vickers 74-2002,283,759 5/1942 Pollard 74-691 2,660,073 11/1953 Patin 74-200 XR3,277,746 10/1966 Forster et a1. 74-730 3,293,945 12/1966 Stockton 747963,406,597 10/1968 Perry et al. 74865 FOREIGN PATENTS 450,246 7/ 1936Great Britain.

LEONARD H. GERIN, Primary Examiner U.S. C1. X.R. 74200, 796

